JPS58113637A - Controller for delay of revolution and vector of force of series damper - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an integrated self-energizing friction delay device for a stretched momentum clutch vibration damper. It is desirable to provide vibration dampers in automobile clutches to eliminate torsional vibrations emanating from automobile engines that can create undesirable shock loads, vibrations, noise, and the like. Such dampers are commonly used in clutches of manual transmissions, and are preferably incorporated into lock-up clutches of torque converters of automatic transmissions.

One example of such a stretched momentum damper is shown in my U.S. Pat. No. 4,279,132.

However, when the driver of a car suddenly releases the accelerator pedal or suddenly depresses the accelerator pedal, sudden forward and reverse torques are generated, which causes the car to rock back and forth and become unsmooth. This results in severe acceleration or deceleration, i.e. tip-in or tip-out of the automobile's clutch.

The present invention eliminates the adverse effects of sudden forward or reverse torques on manual clutches or torque converter lockmap clutches.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a built-in self-energizing rotationally sensitive applied force delay control system for a motor vehicle clutch stretched momentum torsional damper vibration damper to provide proportional delay control. It is to be.

The damper assembly includes a hub member having circumferential radial fingers, a damper housing formed by front and rear retainer plates having inwardly offset drive straps, and between adjacent hub fingers. a set of springs positioned and disposed within the housing, a sliding spring standoff between the sets of springs, and a friction retard plate on each hub finger, the friction retard plates being adjacent; radially movable in engagement with the set of springs and in frictional contact within a channel formed in the housing, the channel extending around the outer edges of the friction delay plate and the spring standoff. It is accommodated.

The present invention also includes a hub member having radial fingers, a friction retardation plate received in each finger, and cooperating engagement surfaces of the fingers and the friction retardation plate, the friction retardation plate being damper. The present invention provides an extended momentum vibration damper assembly adapted to facilitate radially outward movement into frictional engagement with a housing/gun.

The present invention further includes a hub member having radial fingers, a friction retardation plate received in each finger, and a friction retardation plate between the respective knob finger and the friction retardation plate for driving the friction retardation plate radially outwardly. The present invention provides an extended momentum vibrating ring hook assembly having a resilient device that frictionally engages the ring (--a housing).

Still another object of the present invention is to provide the above-mentioned vibration damper assembly which is simplest in construction, efficient, economical, easy to assemble and operate, and reliable; This will become clearer in the explanation.

Embodiments of the invention will now be described with reference to the accompanying drawings.

1 and 2 illustrate the stretched momentum vibration damper assembly 10 of the present invention coupled to a torque input device or attachment ring 11 and a torque output device 12. FIG. When the torque input device is a friction clutch plate of a manual transmission, the torque output device is the input shaft of the transmission, but when the torque input device is the piston plate of a lock-up clutch of a torque converter of an automatic transmission. The torque output device is the hub of the torque converter turbine.

The vibration damper assembly 10 includes a hub in the form of an annular plate or ring 13 with internal splines or teeth 14 on the inner circumference of the bubble ring 13 and a torque output device 1.
Three circumferentially equally spaced radial hub fingers 15 are formed on the outer periphery 16 of the ring 13 for engagement with the ring 2 . Each finger has a pair of generally parallel sides 17 terminating in a flat end surface 18;
It has 17. The hub is located within a vibration damper housing consisting of a front retainer plate 19 and a rear retainer plate 27. The front retainer plate is in the form of an annular ring with a central opening 21, a slightly rearwardly offset circumferential flange 22, and three equally spaced and generally axially aligned hub fingers. It has elongated arcuate slots 23 separated by drive straps 26 which are bent and slightly rearwardly offset. These arcuate slots are each bounded by an outer sloping lip 24 and an inner curved lip 25 to retain a damper spring therein, and a recessed bevel (not shown) is provided with a respective drive strap 26.
The outer lip is formed adjacent to the outer lip.

The rear retainer plate 27 is also in the form of an annular ring and has a central opening 28 and an outer axially forwardly extending wall 29 terminating in a circumferential flange 32.

The flanges 22 and 32 abut each other and are suitably secured to the ring 11 by rivets 33 or the like. The rear retainer plate 27 is provided with elongated arcuate slots 34 separated by three equally spaced forwardly offset drive straps 37. Each arcuate slot is bounded by an outer angled lip 35 and an inner angled lip 36 and serves to retain the damper spring within the housing. The outer lip includes a recessed bevel 38 adjacent each drive strap.

Within the housing there are three groups or pairs of spring sets 39.4.
0 are arranged, and each group is arranged between adjacent nop fingers 15. Each spring set consists of one or more concentric coil springs, such as inner spring 41 and outer spring 42 shown in FIG. A sliding spring standoff 4 between each spring of a group
3 is disposed, the spring standoff piece has a broad-shaped body with outwardly flared sides 44 extending inwardly to an inner end having a central notch 45 for receiving the outer periphery 16 of the bubbling ring 13. It extends outwardly beyond the sides to a narrow arcuate outer edge 46 that extends circumferentially to form ears 47 on opposite sides. A narrow arcuate outer edge 46 and an ear 47 slide within a channel 48 formed in the housing and having an axial wall 29 as the bottom of the channel.

Attached to each radial finger 15 is a friction retardation plate 49 having a generally patterned body with an inner end extending from the finger 15.
It has a deep notch 52 that is roughly complementary to the shape of. The body has outwardly flared edges 53, 53 which terminate in an outer arcuate edge 54 which extends to a circumferential ear 55 and is slidable within the channel 48. The sets of springs 39, 40 on opposite sides of the friction retarding plate 490 engage the edge 53, with the spring load or force vector pointing in the direction perpendicular to the edge 53.
is shown by. This force vector has a radial component that acts to push the friction retardation plate radially outwardly into the channel 48.

The installation is such that when a torque is applied across the ring 11, the housing rotates with the ring 11 and the aligned pairs of drive straps 26, 37 engage the spring set 39;
The spring is pressed against the spring standoff piece 44, which slides within the channel 48 and compresses the spring set 40. spring 40
contacts the side 53 of the friction delay plate 49 and acts on the hub finger 15, causing the hub plate 13 to rotate.

Rotation of the hub plate and fingers acts to push or pull friction retardation plate 49 and channel 48
This resistance is proportional to the centrifugal force due to the mass of the friction retardation grating 49 (arrow B in FIG. 3) caused by engine speed and torque and the force of the spring.

FIG. 4 shows a friction delay plate 49α and a hub finger 15α of a bubbling ring 13α, which is a second specific example. Each radial finger 15a has a pair of sides, a lower parallel portion 17α and an upper sloped engagement edge 56.
It consists of

Similarly, the deep notch 52α of the friction retarding plate 49α has complementary lower parallel edges 57 and an upper sloped engagement edge 58.
has. Thus, in use, when pushed or pulled by the hub finger, the friction retarding plate is affected by the force vector of the spring set (arrow A), the centrifugal force (arrow B) and the engaging edge (arrow C). Actuated by a wedge action to push the friction retardation plate into frictional contact with a channel in the damper housing.

A third embodiment of the delay control device is illustrated in FIG. It is formed at the edge 18h. Friction delay play (49h has a deep notch 52b and a concave bottom 63
and a rounded lateral enlargement 64 is formed to receive an in-field spring 65. This transom spring has an outwardly curved arm 66 , 66 received in opposing recesses 62 , 63 , a central curve 67 received in an enlarged portion 64 , and an end 68 of the arm received in the other enlarged portion 64 . , 68' (r). In this example, the spring force vector and centrifugal force on the friction retardation plate is aided by the spring 650 elastic force.

FIG. 6 shows the radial fingers 15 of the bubbling ring 13C.
A fourth embodiment of the friction retardation plate 49Cf of C is shown, in which the friction retardation plate and hub fingers are substantially the same as shown in FIGS. 1-3. In this embodiment, the finger has an enlarged outer end 7
1, and a gradient coil spring 72 is disposed within the notch 52C of the friction retarding plate between the friction retarding plate and the enlarged end 71 of the radial finger. This canted coil spring functions in the same manner as the in-field spring of FIG.

[Brief explanation of drawings]

FIG. 1 is a partially cutaway rear elevational view of an extended momentum vibration damper assembly including the self-energizing rotationally sensitive applied force delay control device of the present invention. 2 is a cross-sectional view of the damper assembly taken along line 2--2 of FIG. 1; FIG. FIG. 3 is an enlarged rear elevational view of a portion of the hub member including the radial fingers and friction retarding plate showing the force vectors acting on the friction retarding plate; FIG. 4 is an enlarged rear elevational view of a portion of the hub member showing a second embodiment of a modified radial finger and friction retardation plate; FIG. 5 is an enlarged rear elevational view of a portion of a hub member having a second modification of the hub finger and a third embodiment of the friction retardation plate and resilient device; FIG. 6 is an enlarged rear elevational view of a portion of the knob member having the knob finger and friction retarding plate and resilient device of the fourth embodiment; 10... Vibration damper assembly 11... Mounted with a ring or torque input device 12.
...Torque output device 13.13α, 13b, 13C...Bubbling or annular plate 15.15α, 15,6. I5C...Hub finger 19...Front retainer plate 23.34...Circular slot 24.25, 35.36...Lip 26.37...Drive strap 27...Rear retainer Plate 39.40 Spring set 41.42 Spring 44 Spring separation piece 48 Channel 49.49α, 49b, 49C Friction delay plate 55 Ear portion 65 ... In-field spring 72 ... Inclined coil spring

Claims (9)

[Claims] (1) An input member operatively connected to a torque input device (
11), a hub member (13) operatively connected to a torque output device (12) and having at least two circumferentially equally spaced radial fingers (15), and an adjacent... at least one spring spacing piece (43) disposed between the hub fingers and floating independently of the hub member; and a set of compression springs (39, 39) interposed between the hub fingers and the spring spacing pieces. 40), the hub member (13), the spring spacing piece (43), and the spring set (39).
, 40) and operatively connected to said input member (11).
7) and axially aligned axially aligned drive straps (26, 37) mounted on said retainer plate and separated by inwardly offset drive straps (26, 37) adapted to receive and retain said spring set. Elongated arc-shaped slot (2
3, 34) a pickup damper assembly (10) for transmitting torque between a driving and driven member, the damper assembly (10) being supported by a respective hub finger (15) and radially relative to the respective hub finger; outwardly flared edges (53) having reciprocably movable friction retardation plates (49), each friction retardation plate terminating in an arcuate outer edge (54) frictionally engaging said retainer plate;
) A vibration damper assembly comprising: (2) Each said friction retarding plate (49) has a deep notch (52)'(11'') extending from its inner edge to receive a hub finger (15) complementary thereto. Vibration damper assembly. (3) Said retainer plate (19, 27) forms a circumferentially extending channel/I/(48) in which said friction retarding play (49) and said spring standoff piece ( The vibration damper assembly according to claim 1, wherein the vibration damper assembly (43) is slidable. (4) each said hub finger (15) having approximately one parallel side edge (17), and each said friction retardation plate (49) having complementary parallel edges to impart radial movement; A vibration damper assembly according to claim 2, comprising a notch (52) having a notch (52). (5) Said spring sets (39, 40) are connected to the flared edges (5) on opposite sides of each friction retardation plate (49).
3) and is adapted to provide a vector of forces which act to push this friction retardation play H-radially outwardly. (6) Each of the hub fingers (15(Z)
have lower, generally parallel sides (17α), and upper, generally sloped, outwardly contracting engagement edges (56), each friction retardation plate (49α) having a respective complementary parallel side portion (17α); a notch (52) having a lip (57) and an engaging lip (58);
The vibration damper assembly according to claim (2), having α). (7) Vibration according to claim 6, wherein the complementary engagement edges (56, 58) are adapted to provide an additional force vector in addition to the spring force vector. damper assembly. (8) a resilient device (65) in the friction retardation plate (52A) engaging the outer end (61) of the radial hub finger (15A); Vibration damper assembly. (9) The elastic device is an in-field spring (65), and recesses (62, 63) are formed in the end (61) of the hub finger (15b) and the friction delay plate (49A) to accommodate the spring. A vibration damper assembly according to claim 8, wherein the vibration damper assembly is adapted to do the following. Ql The vibration damper assembly according to claim 8, wherein the elastic device is a canted coil spring (72). 0υ said hub member (13) has three equally spaced radial fingers (15) and ears extending circumferentially beyond outwardly flared edges (53) on opposite sides (
The outer edge (54) is shaped like an arc to form (55).
) a friction retardation plate (49) for each said finger having e and between adjacent hub fingers and having a curved body with an arcuate outer edge (46) extending circumferentially beyond said body; and the ears on the opposite sides (47
), and three groups of two sets of springs (39, 40) arranged between adjacent hub fingers (15), forming a respective spring spacing piece ( 4
4. A vibration damper assembly according to claim 3, wherein the vibration damper assembly 3) is arranged between a pair of spring sets. 03. A vibration damper assembly according to claim 00, wherein the groups of springs (39, 40) are arranged to work in parallel and the springs of each group to work in series. 03 The centrifugal force generated by the rotation of the hub member (13) and the force vector of the spring set (39, 40) act on each friction retardation plate (49), causing the friction retardation plate (49) to move outward in the radial direction. The claim is such that the retainer plates (19, 27) are pushed toward each other into frictional engagement within the channels (48) of the retainer plates (19, 27) and provide a resistance to movement proportional to the centrifugal force caused by the engine speed and the force of the spring. The vibration damper assembly according to range 00.